Vibration mechanism and method



Dec. 13, 1966 c. G. MATSON VIBRATION MECHANISM AND METHOD 5 Sheets-Sheet3 Filed Aug. 21, 1964 4&5 L

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INVENTOR. CARL G0 [WATSON BY OMWZM Arr/5 Dec. 13, 1966 c. G. MATSON 9 9-VIBRATION MECHANISM AND METHOD Filed Aug. 21, 1964 5 Sheets-Sheet 5 I NVEN TOR.

w 6, Ma/ao/i 8v UPI Mi W ATTORNEYS United States Patent flice 3,290,952Patented Dec. 13, 1966 3,290,952 VIBRATION MECHANISM AND METHOD Carl G.Matson, Kewanee, Ill., assignor to Vibrator Manufacturing Company, Neponset, Ill., a corporation of Illinois Filed Aug. 21, 1964, Ser. No.391,241 8 Claims. (Cl. 74--87) The present invention relates broadly tofluid actuated mechanical vibration mechanism and method; moreparticularly to a gas-driven rotary device for imparting substantiallysinusoidal vibrations to a part to which it may be attached; and stillmore particularly to an air-driven rotary device including a new methodand apparatus for establishing vibration characteristics and impartingorbital vibrations in a substantially harmonic manner to structuralelements.

This application is related to some subject matter in common with myco-pending application, Serial No. 345,431, filed February 17, 1964.

Machines of this generaltype have been in use for several years and areemployed for facilitating and/or aiding manual transfer of materials inchutes, and the like; are used for vibrating storage bins to settlematerials contained therein and/ or control the movement of materials toand from bins; for enabling convenient un' loading of dump-typeequipment; in foundry work, and the like, for aiding compacting offlasks; and for numerous and varied other purposes.

This particular improved mechanism, to be described in detail below, ischaracterized by being compact while delivering very high frequencyvibrations to articles or things to which it is attached. While thedevice is not to be limited in its broadest concepts, it is preferredthat the single movable element, substantially in the form of a disk,ring, or the like, is operable in a range to create harmonic vibrationsby orbiting in a path of travel predetermined by retaining means for thedevice. The vibrations are preferably in a range exceeding a few orbitalvibrations for each revolution of a rotor but can effect a large numberof vibrations during one complete revolution of the rotor.

The device is further characterized in that the rotor diameter is soselected with relationship to a bore forming a race within which itrevolves to render several orbital vibrations per rotor revolution. Thedevice is further characterized by a transient gas exhaust which orbitswith the rotor to create a new spatial orientation of the rotor in therace with respect to an outlet ecliptic. The eclipic provides arelatively lower pressure air spaced substantially diametrically acrossdiametral segments of the periphery of the disk with relationship to arelatively high pressure area on the opposite side thereof.

In carrying out refinements of this invention, the variably positionedecliptic exhaust, or other conventional exhaust, is sized to cause apressure drop of driving fluid, such as air for example, to expendsubstantially 95% of its energy in the form of pressure in performingthe work creating the orbital vibrations.

Prior vibrators, substantially of the genus of the present invention,have differed in several respects from the present invention inoperating in such manner as to attain by rotors thereof of severalsorts; for example, the ball type rotors set forth in several patentsissued to Edwin F. Peterson, wherein a hard steel ball is restrained bya pair of hardened and ground ra-ceways to control and direct theorbiting of the ball. The construction and arrangement of such vibratorsincludes precise raceways and have attained wide acceptance and havelong life.

The present invention, while hard elements are desirable, is conduciveto manufacture by standard machining procedures (not requiring grindingor hardening of parts) while still providing a long life for the device.Of course, when extra long life is essential in the device, hardenedparts can readily be assembled with certain standard parts of theassembly while providing such features of hardening of the long-livedoperating parts.

Another significant attribute of this invention resides in thecharacteristic of the fluid pressure differential of providing a new andeffective air lubrication of the par-ts, at least in certain ranges ofoperations in which the device is adapted for use.

Accordingly, it is 'a broad object of this invention to provide improvedfluid-driven vibrating devices.

Another object in keeping with the preceding object is to provide anair-lubricated vibrating device.

A further object in keeping with either of the preceding objects is toprovide an improved vibrator adapted to operate at numerous selectedfrequencies of vibrations.

Another object in connection with the preceding object is to provide afluid-driven vibrator operable in highfrequency ranges.

An object in keeping with each of the preceding objects is to provide avibrating device producing high frequencies of orbital vibrations duringeach revolution of a rotor inducing the vibrations.

A further object in keeping with any of the preceding objects is toprovide a rotor in the form of a circular member.

Another object in connection with the preceding object is to provide arotor in the form of a disk or ring, or the like.

A still further object is to provide a raceway integral with a housingfor a rotor operably associated therewith.

Another object in keeping with each of the preceding objects is toprovide a cast metal raceway for vibrators and the like.

Another object of this invention is to provide an improved method fordesign characteristics and/or parameters for vibration apparatus of thecharacter to be described below, as well as other related articles ofmanufacture.

Other objects, features and advantages of this invention reside ininherent attributes of the device and will be either obvious or pointedout in the following specification and claims read in View of theaccompanying drawings in which:

FIG. 1 is a combination of at least two superimposed charts illustratingplural functions of the invention;

FIG. 2 is a vertical sectional view of one form of vibrator takensubstantially on lines 22.' of FIG. 3;

FIG. 3 is a vertical sectional View taken substantially on lines 3-3 ofFIG. 2;

FIG. 4 is a view similar to FIG. 2 of a modification of the invention,and taken substantially on lines 4-4 of FIG. 5;

FIG. 5 is a vertical sectional view similar to FIG. 3, but takensubstantially on lines 55 of FIG. 4;

FIGS. 6, 7 and 8 are diagrammatic views of the modification shown inFIGS. 1 and 2, showing different sized rotors in a given sized bore of araceway;

FIGS. 9, 10 and 11 are diagrammatic views of the modification shown inFIGS. 2 and 4 and having different sized rotors of ring type.

FIG. 12 is an exterior elevational view of a presently preferred form ofthe invention;

FIG. 13 is a sectional view taken on line 13-13 of FIG. 12;

FIG. 14 is an elevational view of a rear side of the invention with arear plate removed; and

FIG. 15 is a view similar to FIG. 14, but with the rotor removed.

Referring now in more detail to the drawings, FIG. 1 is a chart showingcertain of several possible charts that can be superimposed upon oneanother. Because families of curves may be desirable in differentinertia ratios, for example, such families may be placed on transparentmaterial, not shown, over a chart having an orbital characteristiccurve. This latter orbital characteristic is fixed, and therefore as analternative, can conveniently be on transparent material as an overlayfor several family charts.

Orbital vibration plotted with respect to revolutions of a rotor is usedto establish design parameters for uses to which a vibrator including arotor is to be put. A ratio of rotor diameter with relationship to borediameter minus rotor diameter appears on the chart as solid line 15.This line would attain zero at zero percent of diameter of rotor withrespect to the diameter of a bore indicated at the base of the chart.This line 15 will asymptotically approach the right-hand linerepresenting 100% of rotor diameter in which no rotation would bepossible. The right-hand numbers to 60 are representative of orbitalvibrations of a rotor per one revolution thereof with reference to line15. With a rotor diameter approximately 90% of bore diameter someorbital vibrations will occur per rotor revolution.

Superposed with respect to line is a line 16 which is in pound-inchethat is an unbalanced force that varies as a rotor varies away from andback to zero as the rotor diameter varies from zero diameter to 100%diameter of the bore of the vibrating device. It is to be noted when thediameter of the rotor is less than 50% diameter of the bore, representedby the vertical line 1 8 (at 50%) that this curve is linear. The curve16 is selected for a inch thick carbon steel solid disc rotor. In thisarea of the curve to the left of the line 18 as the size or diameter ofthe rotor has increased, its center of gravity with relationship to thecenter of orbit will decrease. Accordingly, the left-hand ordinate ofthe chart is set forth with an x factor which may vary according to thealgebraic characteristic of curve 16 as indicated by lines 16a and 1611.Such variance can be effected by having rotors of one-half the thicknessand double the thickness, respectively, of the A inch thick rotor, andaccordingly a family of curves could he arrived at for use in connectionwith the curve 15 for many thicknesses.

In the example herein used, it may be assumed that the bore diameter isa known whole factor, for example 10 inches in diameter in a largersized vibrator. Wit-h such vibrator, it may be desirable to attain acertain predetermined centrifugal force in order to facilitate and/oreffect movement of a predetermined Weight of material. Accordingly, apoint such as point 20 (lower right side of the chart) may be selectedon the curve 16 representing the one-fourth inch thick rotor. It isnoted that this thickness of rotor has a 2x factor which, in thisexample using a one-fourth inch rotor, would represent two poundinchesof unbalanced weight, with x equaling 1. By projecting verticallydownward from the point 20 on curve 16 to a point 22 on the curve 15, itis to be noted that there are approximately 11 orbital revolutions perone revolution of the rotor.

In cases where a lower number of revolutions are desired, the point 20could be moved to the left to bring the number of orbital vibrationsbelow 10, for example, or could be moved to the right from the positionshown across the point of intersection 25 of lines 15 and 16 where agreater number of orbits per revolution are desired.- However, at suchhigher frequency orbiting the unbalanced weight in pound-inches isreduced substantially and could become about one and one-tenth poundinchat point 26, for example; but the vibrations per rotor revolution, point25 curve 15, will be twenty-one.

In whatever way the selection may be based it is desirable to keep therevolutions of the rotor within an area in that part of the right sideof the chart permitting a wide selection of characteristics best suitedfor different applications of the vibrating apparatus to be described indetail hereinafter. In each selection, however, the user of the methodand device Will be able facilely to calculate the vibration attributesand effectiveness of the device in the selected range.

Method For example only, the points 20 and 22 may be selected, then,with it being within the mechanical capabilities of the rotor to makeabout 900 revolutions per minute, there will be about 10,000 orbitvibrations in each minute. At an unbalanced weight of two poundsoperating at 10,000 revolutions per minute, a centrifugal force of about5,800 pounds will be achieved. With a rotor capable of turning at onlyhalf such speed, for instance, about 500 r.p.m. to again attain 10,000revolutions per minute, a point 25 may be selected on a rotor diameteralong the line 15. Such position indicates 21 orbital vibrations for onerotation of the rotor which projects downward on the line to point 26with a poundinches unbalance of about one and one-tenth pounds.

At this position, 10,000 orbital vibrations per minute the centrifugalforce obtained will be approximately onehalf that obtained in theexample immediately above, or 3,000 pounds. However, as represented bythe line 16b by doubling the rotor thickness to /2 inch, this forcecould be increased to about 6,000 pounds. Centrifugal forces can bereadily ascertained in using this method by a formula C.F.= .0000284Pound-Inch Orbital Vibra tions Squared. The value of CF. thus calculatedis a minute percentage higher than actual centrifugal force. Thepound-inch factor is ascertained by bore radius minus rotor radius timesrotor weight in pounds.

The above specific example is not to be construed in a limiting senseinasmuch as this method of selection Within parameters and/ orcharacteristics adapted for the chart or charts used in both linear andnon-linear ranges. It is preferred that in the linear range theparameter be in different scales because the values, particularly at thelower range of orbital vibrations per rotor revolution, is not varied insuch marked manner as in the non-linear area of the charts describedimmediately above. i

To accomplish the attribute of the invention and facilitate design ofvibrating equipment in accordance therewith, the following Chart A,shown partially only, can be used.

CHART A [Based on 10 diameter bore] 1" Dia. 2" Dia. 3" Dia. 4" Dia. 5"Dia. 6 Dia. 7 Dia.

The above Chart A is based on the example of 10" diameter rotor inchlong. This Chart A can be extended to several lines in known manner toinclude thick' nesses from inch (and thinner) to greater thicknessesthan 4 inch, and may vary greatly in extremely small sized to extremelylarge capacity vibrators. In each such chart, a correction factor can beapplied to the factor x above. For example, a 5-inch bore represents 50%of the above; and hence the two left-hand columns would read one-halfthe value of the numbers shown. The righthand vibration/revolutioncolumn will then be identical as above.

The above Chart A, as well as the curve 15, FIG. 1, of orbitalvibrations for one revolution of the rotor has been arrived atconveniently by development of the following formula: Ratio=d/Dd, WhereD=bore diameter and d=rotor diameter. The orbits create vibrations ofpredeterminable frequency for one revolution of the rotor and is equalsubstantially to the diameter differences of the rotor which traversesthe bore in both an orbital and rotating (manner. Because the rotor mustessentially be Smaller than the bore, the above formula has beenascertained, and has proven substantially accurate for use of thisinvention because the formula inherently includes subtraction of oneorbit per 360 degrees rotation of the rotor. Since pi would appear bothabove and below the division line in the formula, it will divide out.This formula can also be expressed in bore and rotor diametersdifferently thus: D/(Dd)1, for use when it is so prefer-red. In otherwords, one formula is equal to another: d/D1=D/(Dd) 1.

To further facilitate employment of the method of this invention, aChart B is based on a carbon steel disk rotor of diameter maximum forfitting a 10" bore, in keeping with the above disclosure. It is to beunderstood that for larger or smaller diameter disks that correctionfactors for the pound-inch unbalance figures in the body of the chartcan be modified, but that as the relative diameters for a giventhickness vary the pound-inch unbalance will vary as a square function.For example, the 8" diameter rotor, A" thick, in a 10" bore has a threeand one-half pound-inch force. However, a 4" diameter rotor in a 5diameter bore will not read truly as indicated in Chart B at 2% pounds,but would read as a function of the'8" diameter rotor expressed as 3 /2poundinches in Chart B. Because the 4" diameter rotor will haveapproximately one-fourth the weight of an 8" diameter rotor, and willhave an effective eccentric arm of one-half inch in a 5" diameter bore.A different Chart B would need be compiled to accommodate suchdifferences.

CHART B [Based on 10 diameter bore] 1 dia. 2 dia. 3" dia. 4" dia. 5"dia. 6 dia. 7" dia.

To further facilitate practice of this invention, the following Chart Cis set out; which again is in terms of a 10" diameter carbon steel rotorbut setting forth the pound-inch unbalance in percent of bore andpercent of rotor diameters to bore diameters. In the Chart C, thecolumns are headed up along the ordinates in rotor thickness and set.forth in percentage of rotor diameter to the abscis'sae. This chart canbe used additionally for interpolation for different bore and rotordiameters, keeping in mind that as the diameters of these disks change,they vary as a square function of the diameter and accordingly wouldvary according to the basis of ten inches as used in this example.

CHART C.OARBON STEEL POUND-INCH UNBALANCE IN TERMS OF ROTOR THICKNESSBASED ON A 10" DIAMETER BORE Rotor Thickness Rotor Dia. in 0/0 Bore Dia.

% A 1 2 4 %0 lie 1% 1 1% 3% 7 14 28 1V 2% 4% 9 18 36 1% 2 5 1O 20 at 0W5 1% 2% 4% 9% It is to be understood in connection with practicing theabove method that such rotors, because of gyroscopic effects, haveintermittent annular forces acting thereon because the vibrator devicemoves primarily in the sense tending to contain a plane of annularrotation traced by a point on the rotor. However, because the rotoroscillates in this path and is subjected to angular forces outsidethereof due to vibrations induced thereby there are certain precessiveforces of complex nature that tend to cause slippage due to side andedge friction in devices of this type. Such precessive forces are at anangle to the above point-tracedplane, and can attain high values. Themethod calculating suitable forces and stresses for application ofvibrating apparatus and devices in keeping with this formula is enhancedby these secondary forces, and it is desired these be covered by theclaims of this invention.

Mechanism Consider now the details of construction of a first embodimentof the invention with reference to FIGS. 2, 3, 4 and 5. A housinggenerally indicated at may be of cast iron, or other suitable materialhaving favorable strength to Weight to cost attributes, of generallycircular cross section as shown in FIG. 2. The housing 30 has pedestallegs 31 and 32 or the like, provided with holes 33 and 34, respectively,for receiving through bolts, for example, for securing bottom surfaces35 and 36 of the housing 30 to a suitable surface for impartingvibration thereto upon operation of the vibrator 30. A suitable fluid issupplied to a tapped boss 38 into an inlet port 39, which fluid can beany of several, such as air, steam, exhaust gases, etc., to name a few.The device can also be run by liquid such as oil, water, etc., wellknown in connection with this art. The transverse center, FIG. 2, of thecasting St} is provided with an annular internal groove providing atorus path for air; and which also extends completely around a ring 4-1,FIGS. 4 and 5, which may be press fitted in a transverse bore 42 in thecasting 3t The combination of the inlet port 39 and the groove 40 (withor without the ring 41) establishes the useful attribute of thisinvention of separating fluid entrained foreign materials from thedriving fluid, which, for brevity, will be refer-red to as airhereinafter. Several arrangements for the vibrators include quickcoupled hoses, or the like. These can be contaminated in several ways asby being dropped in abrasives, sand, etc., when uncoupled. Onrecoupling, the foreign material can become entrained and blown into thehousing 30. The ring 41 can be positioned to act as a baffle forforeign. material; and the air entering port 39 will centrifuge thematerial. A suitable small outlet port 40:: (which may be tapped andscrew plugged in large and/or for high contaminated service) can expelthe foreign material. The centrifuge driving action of the torus of airin the groove 40 can likewise cause soft particles to be milled topowder upon the cast metal; in which use the outlet port may not berequired. It is to be noted that uses requiring such structure presentlycomprise only a small percentage of the total usage.

The ring 41 at its internal face 44 comprises the bore of the formulaset forth above and graphically illustrated in FIG. 1 and may besuitably machined by known screw machine and/or automatic machine and/orjig and fixture processes, to name a few. It is significant thathardening and grinding steps, and the like, are not required in thisinvention to provide a long-lived vibrator. For certain heavy dutyservice applications of this invention, the internal surface 44 of thering 41 can be hardened and ground to provide an extremely long life andhigh force output in devices of this kind.

The ring 41 is provided with one or more holes 45 which are at theirinner edges preferably substantially tangential with the internalsurface 44 of the ring 41. Accordingly, the fluid entering the hole 39of the boss 38 will pass from the annular recess 40 through the holesand be ejected tangentially of the inner wall 44 of the ring 41 whereinthey tend to cling and follow the inner wall 44 due to a Coanda-effect,which is well-known phenomenon particularly of air and other gases whichtend to follow surfaces. Thus the air, with the parts in the positionshown in FIG. 5, will tend to rotate at high velocity counterclockwisefrom the upper port 45 into an area 47 on the left-hand side of therotor 92. Air also will pass into the lower port 45 adjacent a lowermostposition of travel of the rotor The air will be decelerated and, in theinstantaneous position shown, thus tend to gain in pressure in the area57. Because of aspiration phenomenon, fluid in an area 61 will tend tobe aspirated to a certain degree as it passes toward an ecliptic opening64, preferably opening to each side of the rotors 60 and 92, FIGS. 3 and5.

Because of pressure differential across the rotor 60 between areas 57and 61, which orbits to orbitationally cycle the ecliptic opening 64,there is an air lubrication characteristic apparently across the disk 60and around the sides thereof to be mentioned herein more fully below.

Referring to FIGS. 2 and 3, the rotor 69 is retained by a pair ofclosure plates 65, which may be identical for most purposes, insubstantially a central position in the housing 30 upon the innersurface of the bore 42 which forms a raceway for the rotor 60. Theplates 65 are retained in place around the peripheral edges thereof by apair of snap rings 66 fitting grooves 67 in counterbores in the casting30. Each of the closure plates 65 may have one or more exhaust ports 70communicating with annular grooves 71 on the inner faces of the closuremember 65. The grooves 71 have their outermost edges 72 arranged andpositioned with the peripheral edge 74 of the disk 60 so as to provide alength of ecliptic opening 64 extending between substantially 90 and 120degrees on the periphery 74- of the rotor 60.

It is conventional in this art to supply the vibrator devices with airat substantially 80 psi. pressure. It has been found that, with a rotor60 of A thickness and approximately 9" in diameter, a clearance oftwo-thousandths of an inch on each side thereof with respect to theinternal surfaces of the closure plates 65 apparently causes a film ofair to be retained by molecular wetting of dry material (in the form ofordinary low carbon steel or cast iron or nickel bearing cast iron) andthat air lubrication alone is serviceable and suitable for manyadaptations of the present invention. It is thought, al though notreadily ascertainable, that the pressure difference existing across therotor 60 between the area 57 and the area 61, mentioned above,contributes substantially to this attribute because these areas are alsocaused to orbit rapidly at the rate of orbiting of the rotor 60, atleast in rotors having approximately 90% of the diameter of the bore inwhich they rotate, and the attribute and phenomenon probably prevailsubstantially above and below such 90% value.

In operation of the modification shown in FIGS. 2 and 3, air isintroduced under pressure which, in starting the rotor 60 from rest,causes a pressure build-up in the area 57 in excess of the pressurebuild-up in the area 61 which is shown communicating with the opening64. The device will start up so long as there is enough air supply inexcess of escape thereof through the exhaust port 64 to cause the rotor60 to be urged toward the right and upwardly in a path of orbit 75around the center point of the rotor 60.

When orbiting, a rotor 60 will roll along a dotted line 66 as the edge74 thereof frictionally contacts the internal surface of the bore 42. Aspointed out in con nection with FIG. 1, the number of orbits per revolution are determined by the diameter differences of the bore 44 and thesurface 74. It has been found that an exhaust pressure out of theorbiting ecliptic opening 64 can be approximately 5% of that of theinput pressure (in this case about four pounds per square inch) and theair will pass through channel 71 and out of exhaust ports 70 toatmosphere after having expended about 95% of its energy due topressure.

As mentioned above briefly, this invention can utilize certain metalsfor parts as machined for many adaptations thereof. When an intermediatedegree of hardness of relatively movable surfaces is desired, such partscan conveniently be fabricated from nickel-iron alloy irons or steels,or other known alloys having work hardening characteristics. Manynickel-iron alloys having such desirable characteristics for thisinvention work harden during use of a vibrator. Relatively movable,force effected, parts such as the bore 42 and rotor 60, at least, andretainer plates 65 when gyroscopic conditions prevail, can be made ofthese alloys. When cold fiow during work hardening is a characteristicof the alloy, the edges of the rotor 60 are preferably relieved, as bychamfering in well-known manner, not shown, to accommodate metaldisplaced during work :hardening. Of course, for high reliability use ofthe invention, either conventionally hardenable or some of the so-calledexotic metals can be utilized.

FIGS. 4 and 5 show a modified form of the invention and include aperforated disk to facilitate a bolt assembly, and is particularlyuseful in certain capacity vibrators and in several applicationsthereof. This form of the invention has many characteristics similar tothe first form above. Perforated disks, for example, can also be used inthe first form to attain desired weight per diameter and/or to providedesired gyroscopic characteristics.

A casting may be substantially identical in the center portion thereofas viewed in FIG. 4, but for a given size can be thinner than that ofthe modification described above. The casting 80 has a peripheral centergroove 82 to which air is supplied under pressure through a boss 83 inthe casting. The casting 80 is mounted in any suitable manner such as bylegs 84 having a bottom surface adapted to engage a device to bevibrated.

The casting 84 has a pair of opposite substantially identical shoulders85 in which internal flat faces of a pair of sealing plates 86 areadapted to abut. Each sealing plate 86 has an annular groove 88 as andfor the same purpose as the grooves 71 of FIGS. 2 and 3 and likewisecooperable with the peripheral edge 90 of a ring-shaped rotor 92, whichrotor has a central hole 93. A bolt has a head 96 engaging one plate 86and a suitable lock nut 98 engages the other plate. The bolt 95 passesthrough the hole 93 in the rotor 92 and is provided with ample clearancewith respect thereto in all positions of the rotor 92 to prevent contacttherebetween at all times. The edge 90 of the rotor 92 will ride on theinternal surface 44 of the ring 41 to provide an orbital path 99 for thecenter of gravity of the rotor 92 while the same rotates in thedirection of the broken line arrow 100.

In operation, the modification of FIGS. 4 and 5 is substantiallyidentical to that of the modification shown and described in connectionwith FIG. 2, but does have a different gyroscopic moment inasmuch as thehole 93 may be of greater or lesser diameter whereby to concentrate thegyroscopic-force-creating mass-domains nearer to the periphery 90 of therotor 92 as the hole 93 is enlarged. As is well known, the gyroscopicformula follows a diameter squared mathematical formula; and when thedisk comprising the rotor is solid, this portion of the formula isdivided by a factor of two. If all of the metal providing mass isconcentrated at the rim comprising the edge 90, the gyroscopic formulawould read simply diameter squared. Of course, this is not possible.

As mentioned above, the exact nature of gyroscopic precessional forcescreated in the several rotors may vary substantially depending upon thedegree of movement of the vibrator bodily as it vibrates an object towhich it is attached. This is further complex inasmuch as vibrationsinduced in one plane can gyroscopically cause secondary vibrations innon-parallel planes which effect the surface supporting the vibratingequipment and accordingly render the resultant vibrations multi-phaseand multi-planar. The not readily ascertainable :multi-vibrationsdepending upon the orbits of the rotor 92 per unit of time (which unitestablishes a primary mode of vibration in a first plane parallel to thepaper as viewed in FIG. also creates precessional vibrations due to thegyroscopic action of the rotor 92 as it makes rotations (incontradistinction to orbital vibrations) per unit of time. In themodification of FIGS. 4 and 5, the orbital induced vibrations around thepath 99 are always greater in number than the revolutions of the rotorbecause the ring 92 is essentially larger in at least the preferred formof this modification of the invention such as shown in FIGS. 4 and S,and in diagrammatic form in FIGS. 9, and 11. It is to be understood,however, that the rings can be smaller to operate in the linearfunctions area of the chart, FIG. 1.

With the modification shown in FIGS. 4 and 5 in operation, the air isintroduced through ports 45 in the ring 41 to cause orbiting androtation of the rotor 92 about the raceway surface 44. The air will exitthrough an ecliptic opening 102 to be exhausted through one or moreoutlet ports 103 in each of closure plates 86; substantially identicalto the function and at pressure drop values explained in connection withFIGS. 2 and 3.

With reference again to FIGS. 2 and 3, the rotor 61) explained thereinwas assumed to be operating within the area defined by points 20, 22, 26and 25, FIG. 1, and may be approximately 93 percent of the diameter ofthe bore defined by the raceway surface 44. As pointed out more indetail in connection with FIG. 1, the desired forces are selected and asuitable rotor diameter picked after determination of permissiblerevolutions of the rotor and desirable high-frequency orbital vibrationsinduced by orbiting of the rotor. It is to be further noted inconnection with the details of construction of FIG. 3 that, from a pointof contact 1115 on the rotor 60 as a reference, the rotor 60 will becaused to pass through 360 degrees of rotation of the rotor many timesbefore returning to the exact position shown. By selecting a non-evenlydivisible ratio of the bore diameter to the rotor diameter, such point105 may be caused not to re-register regularly with a point 106 withwhich it is shown in registry, FIG. 3. By properly selecting thediameters of the bore defined by the surfaces 42 and 44, FIGS. 3 and 5respectively, the point 105 may migrate with respect to the point 106 sothat a very high number of revolutions of the rotors 6t) and 92 will berequired before the points 105 and 1% reregister with respect to eachother.

Because of the rotation characteristic mentioned above, ordinary (notprecise) machine finishes of both the surfaces 42 and 44 and theperipheries '74 and 90 of the rotors 60 and 92 can be tolerated. Oncontinued operation of such a device, irregularities of either of thecontacting 1% surfaces are not inclined to become aggravated by frequentcontact one with the other. In fact, small imperfections andirregularities will be worn away and are self-correcting in this device.

Referring now to FIGS. 6, 7 and 8, solid rotors 60a, 60b and 600 areshown as being in rings 41 for orbiting around paths 75a, 75b and 75crespectively, and the edges of the disks 60a, 60b and 6110 are arrangedto cooperate with outlet ports 64a, 64b and 640 respectively, in arotary ecliptic manner substantially the same as mentioned and describedin connection with FIGS. 2 and 3. These rotors 641a, 60b and 60c willeach require a somewhat modified annular relationship with respect tothe diameter of the slot 64a forming an ecliptic to provide a pressuredrop through the different rotors of substantially 95 percent of thepressure of the inlet driving fiuid therefor, at least when the drivenfluid is air or other gas having similar frictional flowcharacteristics.

It is to be noted that the rotor 60a, 60b and 600 of FIGS. 6, 7 and 8,respectively, are respectively smaller in diameter and accordingly havea less percentage of diameter as interpreted with regard to FIG. 1. Theapparatus arranged as shown in FIGS. 6 and 7 will have non-linearcharacteristics residing on the right-hand side of the line 18 at arotor diameter of percent of the diameter of the bore (surface 44 ofFIG. 2). It is further to be noted that these rotors having diametersthat lie substantially at the peak of the curve 1 5, FIG. 1, andaccordingly have the greatest pound-inch unbalance. It is to be notedhowever that these rotors will also lie in the area. of only a feworbital vibrations to one revolution of the rotor, and accordingly thefrequency of vibration will be correspondingly low. This is not adisadvantage in many adaptations of this device and is highly desirablein certain of them.

The device shown in FIG. 8 is sized so as to have less than one orbitalvibration per one revolution of the rotor c and accordingly thecharacteristics thereof lie on the left-hand side of line 18, FIG. 1. Inthis form of the invention, the upper peripheral surface 740 is lessefficacious in the ecliptic exhaust port function, and any smallerrotors would be provided only with a given size exhaust orifice at thecenter of the closure plates 65 to maintain substantially a percentpressure drop through the device in keeping with the teachings of thisinvention.

FIGS. 9, 10 and 11 represent selected perforated rotors applicable inthe modification of the invention described above and shown in FIGS. 4and 5. FIGS. 9, l0 and 11, respectively, show vibration-inducing rings92a, 92b

and 920 of respectively increasing outside diameters with.

successivly decreasing internal diameters. It is to be understood inkeeping with the practice of this invention that there are a multitudeof possibilities of different configurations of the rings 92, 92a, 92band 92c in keeping with selections that are made by use of the chart ofFIG. 1 or charts that can be constructed in keeping with teachings setforth above in the specification.

FIGS. 12 to 15 inclusive represent a presently preferred embodiment ofthe invention now to be described. A casting may be of suitable gradecast iron, heattreated cast iron, nickel cast iron, or steel forheavy-duty service. The casting 10 has an axial bore 112 therethrough,which bore 112 provides a large contact surface for a rotor 115 whichrides around the bore 112 and momentarily contacts different areas 114in its orbit. As the diameter of the rotor more closely approaches thediameter of the bore, the areas 114 increase in size and distributeforce over larger areas 114. The bore 112 has shoulder formingcounterbores 116 at each side or face of the casting to provideshoulders spaced apart a predetermined distance to be explained morefully hereinbelow. A boss 118 is suitably drilled and tapped forreceiving a supply pipe connecting fitting, not shown, for supplyingpressurized gas or air through an orifice 120 to the interior of thecasting 110. The pressurized air 1 1 drives the rotor 115 incounterclockwise orbit while the rotor 115 rolls in a clockwise senseupon the bore 112 forming a raceway for the rotor 115.

A pair of cast plates 125 may be cast substantially identically withrespect to each other to provide air passageways 126 for air to exhaustaround and within a bore 128 in the rotor 115. One of the plates 125 isdrilled through to provide spaced apart outlet ports 128a, there beingfour shown in FIGS. 14 and 15.

The left-hand plate 126 is drilled and tapped threads 130 at its centerreceive the threaded end 132 of a machine screw 134. The right-handplate 125 is provided with a larger hole 134 to receive the shank of thescrew 134. The head 138 of the screw 134 bears against a plate 140 whichcan serve as a label plate and also a diffuser for exhaust air issuingfrom the outlets 128a. A Belleville washer 142 is arranged to becompressed between the inside face of the plate 140 and the exteriorsurface of the right-hand cover plate 125. The washer 142 serves tospace the plate 140 from the face of the right-hand plate 125 and also.pressure locks the threads 130 to the threaded end 132 of the screw 134.

As shown in FIG. 14 an ecliptic 145 follows the orbiting path and pointof contact 114 of the rotor 115 by 180 degrees. As shown in FIG. 14 theair issuing from jet 120 will blow downwardly and diffuse against theleft-hand side of the rotor 115 and thereby expand and increase inpressure to urge the rotor 115 to roll clockwise and upward and towardthe right from the area of contact 114 and thus into orbit with theecliptic opening 145 following instantaneous areas of contact 114 by 180degrees.

A spacer 147, and additionally the shoulders of the counterbores 116, oralternatively one or the other, are spaced apart the length of the rotor115 from left to right as viewed in FIG. 13 and provide a clearance ofone or two-thousandths of an inch between the right and left side facesof the rotor 115 which are flat, preferably. The inside faces 127 of theplates 125 are correspondingly flat to maintain this slight clearance inthe entire orbital path traced by side faces of the rotor 115.

It has been found in this invention, even with castiron castings 110 andparticularly so in nickel-containing cast irons and steels, that thesurfaces 112, when traversed by a steel rotor 115, take on a burnish orhigh polish after continued use of a vibrator. The exact phenomenon inconsideration of cast iron has not been completely analyzed, but itappears that a very low rate of wear of steel from the rotor 115 as ittravels along the raceway 112 interstitially combines with and migratesI and pressure Welds into pores in the cast-iron raceway 112 to depositand build therewithin and thereupon a hard steel surface; and thiscomprises another attribute and advantage of this invention.

By the nature of the casting and the amount of volume of air flowing inpassageways 126 in the interior faces of the plates 125 and around sidefaces of the rotor 115, the passageways 126 and subpassageways 126aleading to the outlet openings 128a may be left in as-cast condition asindicatetd by dotted surface shading in FIGS. 14 and 15. However, formost precise operation these surfaces may be machined to present lessresistance to flow of air or other gas around the sides of the rotor115.

As mentioned briefly above, four outlet openings are illustrated inFIGS. 14 and 15. It is to be understood that more than four openings orless than four openings may best suit different uses to which thisvibrator may be put. As noted in connection with the description of theother modifications hereof, this vibrator likewise uses a smallerquantity of pressurized air than the ball Wpe vibrators of the priorart.

It is noted in each of the modifications described hereinabove that therotors orbit in a counterclockwise direc tion while the rotor rolls uponthe raceways in a clockwise rotation. Accordingly, it appears that thegyroscopic forces generated are to some extent compensatory andoffsetting with these two different modes of orbiting and rotating. Itis to be noted, with reference to FIG. 1, as the rotor diameter attainsof bore diameter that there is a ratio of 10:1 between 360 degree orbitsand one complete rotation of a rotor in an opposite sense of rotation.At approximately 85% ratio of rotor diameter to bore diameter it is tobe noted that about a 5:1 ratio of orbits to rotations obtains. At the50% ratio of rotor diameter to bore diameter, which is attainable in themodifications shown in FIGS. 2 and 3, there is one orbit per onerotation of the rotor. While the exact nature of the gyroscopic effectsand the degree of compensation thereof is still in the experimentalstage this appears to be an important attribute of the invention thatcan be made of particular utility because the disk-type rotors are airlubricated at their sides to thereby reduce friction loss factors inthis invention, and accordingly the gyroscopic forces, includingprecession and mutation, effect force against a film of air.

Although each of the forms of the modifications of the above-describedvibrators have been shown in an upright position, these devices arecapable of operating in all positions of orientation. It may bedesirable, when the forms are constructed and arranged to provide highgyroscopic forces, that a lubricating medium other than air, such as oilor the like be entrained with the air, or other gas, or used as thedriving fluid.

Each of the modifications described above avail significant newattributes. Vibrators of this kind attain high eflicacy when operatingat high r.p.m.; because the law of centrifugal force contains an r.p.m.squared factor. As pointed out briefly above, the herein-disclosedvibrators operate at the highest r.p.m. when the rotors contact amaximum area of raceway. Accordingly, the higher centrifugal forces aregenerated wtih large surface contact; preferably, though not in alimiting sense, from a rotor diameter of 70 to percent of bore diameter.

Another attribute of the invention, in connection with the aboveattribute, resides in the provision of a small number of different partsto be stocked by a manufacturer or user of the vibrators. For example,rotors match castings and/ or raceway rings and closure plates, but notessentially the latter. Rotors cooperate with castings and/or racewayrings for different characteristic modes of the vibrators. The closureplates, further, can be shouldered (not shown) so as to accommodatedifferent lengths (thicknesses) of rotors. Parts can therefore bestocked, for example, according to casting sizes, and convenientlycataloged and coded as 10', 9", 8", etc., to a desirable minimum inraceway lengths (corresponding to rotor length +.004", for example) of5", 4", /2, etc. The rotors and closure plates may be similarly coded,with same bearing percent of bore diameter.

In accordance with the above example used in connection with FIG. 1, inkeeping with a code system such as immediately above, a vibrator forproviding a centrifugal force of 6,000 pounds, at 10,000 orbitalvibrations per minute, could be coded as 10- Az95. This represents a10-inch bore, /2 inch long, and a rotor of 95% of bore diameter.

In keeping with the teachings above, a mechanic or machine operator canexchange and/ or replace parts to change vibrator characteristics. Thebody does not necessarily need to be removed to make such change,particularly when excess forces are being generated. For example, if itis desired to reduce the capacity of a l0 /z95 vibrator, differentassemblies may be made. A 10 /2875 would require only an 8.75 rotor; orother rotor diameters could serve more aptly. If a 9- inch bore isindicated as more apt, a 10-inch outside diameter raceway ring andsmaller rotor may be best; etc., and designated wtih 10R9 code, or thelike.

If a shorter (thinner) rotor is indicated, shouldered 13 closure platesmay be used therewith to efiect the change while using the same casting;and these examples represent only a few of the possibilities of thisinvention.

While I have shown and described in detail two modifications of thisinvention and a method of ascertaining and/or selecting rotor structuresin terms of unbalanced weight in pound-inches Wtih respect to diameterof a rotor in percent of diameter of bore, further in consideration ofthe number of orbital vibrations to be obtained per one revolution ofthe rotor, and at least one manner for conveniently practicing themethod to provide devices for a multiple of uses, obviously othermodifications and adaptations of this invention will occur to othersworking in the art. Accordingly, I wish not to be limited in myinvention only to the specific forms and methods described above, but bythe scope and spirit of the following claims.

I claim:

1. A pressurized-fiuid-driven vibrator comprising a housing having apressurized-fluid inlet, a pair of side closure members for saidhousing, said housing and closure members together forming a generallycylindrically walled and at least partially flat and parallel-endedclosure, a perimetrically-cylindrical disc-shaped centrallyperforatedrotor confined for rolling movement upon the perimetrical edge of sameupon the cylindrical wall of said enclosure, said centrally perforatedrotor being greater in perimetrical diameter than the radius of thecylindrical wall of said housing, and means carried by at least one ofsaid closure members forming an outlet for fluid from said enclosure.

2. A vibrator generally as set forth in claim 1, and means passingthrough the perforation in said rotor for connecting said closuremembers.

3. A vibrator generally as set forth in claim 2, and spacer meanssecured by said connecting means preventing said closure memberstouching opposite sides of said rotor simultaneously.

4. A vibrator generally as set forth in claim 1, and a diffuser foroutlet fluid secured adjacent said outlet by said closureinterconnecting means.

5. A vibrator generally as set forth in claim 1, said housing being madeof cast iron, and said cast iron containing nickel to render same workhardenable.

6. A vibrator generally as set forth in claim 1, at least one of saidclosure members having an inwardly facing annular shoulder therein, anda perimetrical edge of said rotor cooperable with said shoulder to forman orbiting outlet passage for fluid flow when the rotor is driven inorbit.

7. A vibrator generally as set forth in claim 1, the perimetricaldiameter of said rotor having at least sixty percent ratio to thediameter of the cylindrical wall of said housing, whereby providingcontact area between same having a characteristic of increasing in areaas said percent ratio increases.

8. A vibrator generally as set forth in claim 7, said area increasingcharacteristic being a non-linear function increasing toward one hundredpercent ratio.

References Cited by the Examiner UNITED STATES PATENTS 2,136,946 11/1938McCurdy 29-149.5 2,179,824 11/1939 Kip 308-362 2,198,148 4/1940 Baily259-1 2,735,165 2/1956 Soref et al. 29407 2,793,009 5/1957 Peterson259-1 2,891,775 6/1959 Molan 259-1 2,906,016 9/1959 Cannon et al. 294072,960,314 11/1960 Bodine 74-87 X 3,069,750 12/1962 Koppelman 29-90 ,1246/1964 Sartor et al. 74-87 3,139,101 6/1964 Wyczalet 134-186 3,166,7721/1965 Bodine 15-22 3,171,634 3/1965 Malan 259-1 FRED c. MATTERN, 111.,Primary Examiner.

BROUGHTON G. DURHAM, Examiner. F. E. BAKER, Assistant Examiner.

1. A PRESSURIZED-FLUID-DRIVEN VIBRATOR COMPRISING A HOUSING HAVING APRESSURIZED-FLUID INLET, A PAIR OF SIDE CLOSURE MEMBERS FOR SAIDHOUSING, SAID HOUSING AND CLOSURE MEMBERS TOGETHER FORMING A GENERALLYCYLINDRICALLY WALLED AND AT LEAST PARTIALLY FLAT AND PARALLEL-ENDEDCLOSURE, A PERIMETRICALLY-CYLINDRICAL DISC-SHAPED CENTRALLYPERFORATEDROTOR CONFINED FOR ROLLING MOVEMENT UPON THE PERIMETRICAL EDGE OF SAMEUPON THE CYLINDRICAL WALL OF SAID ENCLOSURE, SAID CENTRALLY PERFORATEDROTOR BEING GREATER IN PERIMETRICAL DIAMETER THANT THE RADIUS OF THECYLINDRICAL WALL OF SAID HOUSING, AND MEANS CARRIED BY AT LEAST ONE OFSAID CLOSURE MEMBERS FORMING AN OUTLET OFR FLUID FROM SAID ENCLOSURE.